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(A)HEAT TRANSMISSION LOAD(E) REQUIRED COMPRESSOR CAPACITYSidewalls:40’ x 8’ x 2 = 640 Ft 2 x60°TD x 1.9 (Table 7A)= 72,960 BTU10’ x 8’ x 2 = 160 Ft 2 x60°TD x 1.9 = 18,240Ceiling:40’ x 10’ = 400 Ft 2 x 60°TDx 1.9 = 45,600Floor:40’ x 10’ = 400 Ft 2 x 15°TDx 1.9 = 11,400Total 24 hour transmission load = 148,200(B) AIR INFILTRATION3000 Ft 3 x 9.5 air changes(Table 8) x 2 usage factor x2.11 factor (Table 9) 120,270 BTU(C) PRODUCT LOAD500 lbs. bacon x .50 sp.ht. (Table 10) x 10°TD = 2,500 BTU15,000 lbs. beer x 1.0 sp. ht.(Table 10) x 40°TD = 600,000 BTU500 lbs. lettuce x 2700BTU/24 Hr/Ton (Table 10) =675 BTU1,000 lbs. beans x 9700BTU/24 Hr/Ton (Table 10) = 4,850 BTUTotal 24 hour Product Load 608,025 BTU(D) SUPPLEMENTARY LOAD24 Hour Load:Heat Transmission148,200 BTUAir Infiltration 120,270Product 608,025Supplementary 62,544Total 24 Hour Load 939,039 BTURequired compressor capacity:Based on 16 hour operation58,690 BTU/Hr.RELATIVE HUMIDITY AND EVAPORATOR TDRelative humidity in a storage space is affected bymany variables, such as system running time, moistureinfiltration, condition and amount of product surface exposed,air motion, outside air conditions, type of systemcontrol, etc. Perishable products differ in their requirementsfor an optimum relative humidity for storage, andrecommended storage conditions for various productsare shown in Tables 13 and 14. Normally satisfactorycontrol of relative humidity in a given application can beachieved by selecting the compressor and evaporatorfor the proper operating temperature difference or TDbetween the desired room temperature and the refrigerantevaporating temperature.The following general recommendations have provento be satisfactory in most normal applications:DesiredTDTemperature Relative (RefrigerantRange Humidity to Air)25°F. to 45°F. 90% 8°F. to 12°F.25°F. to 45°F. 85% 10°F. to 14°F.25°F. to 45°F. 80% 12°F. to 16°F.25°F. to 45°F. 75% 16°F. to 22°F.10°F. and below — 15°F. or less200 Watts x 12 hours x 3.41BTU/Hr1/2 H.P. x 4250 BTU/Hr-Hr(Table 16) x 242 People x 2 Hrs/Day x 840BTU/Hr (Table 17)Total 24 hour SupplementaryLoad8,184 BTU51,000 BTU3,360 BTU62,544 BTUCOMPRESSOR SELECTIONIn order to select a suitable compressor for a givenapplication, not only the required compressor capacitymust be known, but also the desired evaporating andcondensing temperatures.Assuming a desired relative humidity of 80%, a 14° TDmight be used, which in a 40°F. storage room resultin evaporating temperature of 26°F. To provide somesafety factor for line losses, the compressor should beselected for the desired capacity at 2°F. to 3°F. belowthe desired evaporating temperature.© 1968 Emerson Climate Technologies, Inc.All rights reserved.16-2
The condensing temperature depends on the type ofcondensing medium to be used, air or water, the designambient temperature or water temperature, and thecapacity of the condenser selected. Air cooled condensersare commonly selected to operate on temperaturedifferences (TD) from 10°F. to 30°F. the lower TD normallybeing used for low temperature applications, andhigher TDs for high temperature applications where thecompression ratio is less critical. For the purposes ofthis example, a design TD of 20°F. has been selected,and in 100°F. ambient temperatures, this would resultin a condensing temperature of 120°F.COMPONENT BALANCINGCommercially available components seldom will exactlymatch the design requirements of a given system, andsince system design is normally based on estimatedpeak loads, the system may often have to operate atconditions other than design conditions. More thanone combination of components may meet the performancerequirements, the efficiency of the systemnormally being dependent on the point at which thesystem reaches stabilized conditions or balances underoperating conditions.The capacities of each of the three major systemcomponents, the compressor, the condenser, and theevaporator, are each variable but interrelated. Thecompressor capacity varies with the evaporating andcondensing temperatures. For illustration purposes anair cooled condenser will be considered, and for a givencondenser with constant air flow, its capacity will varywith the temperature difference between the condensingtemperature and the ambient temperature.The factors involved in the variation in evaporator capacityare quite complex when both sensible heat transferand condensation are involved. For component balancingpurposes, the capacity of an evaporator whereboth latent and sensible heat transfer are involved (awet coil) may be calculated as being proportional to thetotal heat content of the entering air, and this in turn isproportional to the wet bulb temperature. For wet coilconditions, evaporator capacities are normally availablefrom coil manufacturers with ratings based on the wetbulb temperature of the air entering the coil. For conditionsin which no condensation occurs (a dry coil) theevaporator capacity can be accurately estimated onthe basis of the dry bulb temperature of the air enteringthe coil.Some manufacturers of commercial and low temperaturecoils publish only ratings based on the temperaturedifference between entering dry bulb temperature andthe evaporating refrigerant temperature. Although frostaccumulation involving latent heat will occur, unless thelatent load is unusually large, the dry bulb ratings maybe used without appreciable error.Because of the many variables involved, the calculationof system balance points is extremely complicated. Asimple, accurate, and convenient method of forecastingsystem performance from readily available manufacturer’scatalog data is the graphical construction ofa component balancing chart. The following exampleillustrates the use of such a chart in checking the possiblebalance points of a system when selecting equipment.To illustrate the procedure, tentative selectionsof a compressor, condenser, and evaporator have beenmade for the sample load previously calculated.Figure 69 shows the compressor capacity curves aspublished by Emerson Climate Technologies, Inc. onthe Copeland® brand compressor specification sheet.It should be noted that Copeland® brand compressorcapacity curves for Copelametic® compressors arebased on 65°F. return suction gas. In order to realize thefull compressor capacity, the suction gas must be raisedto this temperature in a heat exchanger. If the suctiongas returns to the compressor at a lower temperature,or if the increase in suction gas temperature occurs dueto heat transfer into the suction line outside the refrigeratedspace, the effective compressor capacity will besomewhat lower. In the example, the desired capacitywas 58,690 BTU/hr. at 24°F. evaporating temperatureand 120°F.condensing temperature, and this compressorwas the closest choice available, having a capacityof 57,000 BTU/hr. at the design conditions.Figure 70 shows the same compressor curves, withthe condenser capacity curves for the tentative condenserselection superimposed. From the condensermanufacturer’s data, condenser capacity in terms ofcompressor capacity at varying evaporating temperaturesare plotted, and the condenser capacity curves canthen be drawn. Note that the net condensing capacitydecreases at lower evaporating temperatures due tothe increased heat of compression.It is now possible to construct balance lines for the compressorand condenser at various ambient temperaturesas shown in Figure 71. For an ambient temperatureof 100°F., point A would represent the balance pointif the compressor were operating at a suction pressureequivalent to a 28°F. evaporating temperatureand 120°F. condensing temperature. At this point thecapacity of the condenser would exactly match that ofthe compressor at a 20° TD (condensing temperatureminus ambient temperature). The balance point is determinedby the intersection of the 20°F. TD condensercapacity curve with the compressor capacity curve for(continued on p. 16-9)16-3© 1968 Emerson Climate Technologies, Inc.All rights reserved.
Page 2 and 3: FOREWORDThe practice of refrigerati
Page 4 and 5: INDEX OF TABLESTable 4 Typical Heat
Page 7 and 8: VALUES OF THERMAL CONDUCTIVITY FORB
Page 9 and 10: 12-5© 1968 Emerson Climate Technol
Page 11 and 12: 12-7© 1968 Emerson Climate Technol
Page 13: QUICK CALCULATION TABLE FORWALK-IN
Page 16 and 17: © 1968 Emerson Climate Technologie
Page 24 and 25: LATENT HEAT OF FREEZINGThe latent h
Page 30 and 31: Section 15SUPPLEMENTARY LOADIn addi
Page 42 and 43: Table 18Table 19© 1968 Emerson Cli
Page 44: Form No. AE 103 R3 (10/06)Emerson®

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